JPH0972451A - Pressure control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make accurate load setting of a spring of a spring in a pressure control valve and prevent generation of a deviation after setting. SOLUTION: A load setting means consists of a receiving plug 40 to be screwed into a valve body 10 which compresses a spring, and a retaining member 60 which locks the receiving plug 40 and is fixed on the valve body 10. Locking can be achieved by engaging, with each other, the recessed part D of an indexing part 41 which is formed at the receiving plug 40 and whose rotational direction is finely-divided and the protruding part P of the retaining member 60.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure regulating valve, and more particularly to a spring load setting means in a solenoid valve type pressure regulating valve.

[0002]

2. Description of the Related Art Generally, a solenoid valve type pressure regulating valve operates a valve element by a mutual relation between a load by an electromagnetic solenoid, a spring load and a feedback hydraulic pressure, and supplies a pressure supplied from an input port to an electric signal input to the electromagnetic solenoid. The pressure is adjusted to an output pressure corresponding to and output from the output port. In such a valve, in order to keep the characteristics of each product of input signal versus output hydraulic pressure due to machining error of the valve body, valve body, spring, electromagnetic solenoid, etc., variation of load characteristics with respect to input signal of electromagnetic solenoid, etc. within a predetermined allowable range. And a load setting means utilizing that the compression load of the spring is mechanically adjustable.

Conventionally, as an example of such a load setting means, there is a technique disclosed in Japanese Patent Application Laid-Open No. 3-204488. In this technology, a spring that abuts the valve body is supported in a compressed state by a receiving plug screwed into the end of the valve body, and is received by a cantilevered plate spring portion of a holding member that is fitted in the valve body to prevent rotation. The hexagonal indexing head projectingly formed on the outer end of the stopper is clamped at the opposite parallel indexing surfaces to prevent the stopper from rotating with a predetermined screwing stroke. As it is, rotate the indexing head against the clamping force of the leaf spring part, and screw in or unscrew to adjust the screwing stroke of the receiving plug to change the spring compression amount. It is a setting means that can adjust the spring load to be fixed again by the pinching force of the spring.

[0004]

By the way, in the above-mentioned load setting means of the prior art, since six indexing surfaces per rotation by the hexagonal indexing head are used, one indexing surface of the receiving plug is moved to the next. The rotation angle to the indexing surface of is 60 °,
The minimum amount of change in hydraulic pressure that can be changed between the adjacent indexing surfaces in relation to the screw pitch is naturally limited. FIG. 6 shows the relationship between the signal current I (specifically, the duty cycle% of the current) and the output hydraulic pressure P (kgf / cm ² ) in such a valve, and the allowable range of the output hydraulic pressure error for each current value is ± If b is set, the hydraulic pressure characteristic cannot be within the allowable standard range unless the hydraulic pressure variation a corresponding to the rotation angle of 60 ° of the receiving plug is a <| 2b |.

Recently, for example, a linear solenoid valve, which is incorporated in an automatic transmission mounted on a vehicle and is used as a pressure control valve for controlling the hydraulic pressure thereof, has become complicated and sophisticated in control of the automatic transmission. As a result, the allowable range of the hydraulic pressure output error becomes smaller, and higher precision is required. Therefore, the spring load must be adjusted more finely than the spring load adjustment in the prior art. For that purpose, it is conceivable to make the indexing head of the receiving plug more polygonal and to increase the number of indexing surfaces per one rotation.

However, if the number of indexing surfaces is simply increased, the shape becomes more circular. That is, since the length of the index surface in the rotation direction becomes shorter as the number of angles increases, the contact area between the holding member and the leaf spring portion becomes smaller, while the ridge angle between the index surfaces becomes obtuse as the number of angles increases. Therefore, the resistance required for the leaf spring portion to cross the ridge angle is reduced, and the receiving plug is easily rotated by an external force. Furthermore, since the receiving plug for setting the spring load receives the reaction force due to the compression of the spring, it always receives the force to unscrew the receiving body, that is, the force to unscrew the receiving cap, so that the pressure regulating valve is installed in the part with a lot of vibration. In this case, the spring load may rotate due to the vibration even though it is elastically sandwiched by the leaf springs, and the spring load setting may deviate from the initial setting position and may be incorrect.

Therefore, it is a first object of the present invention to provide a pressure regulating valve having a spring load setting means which is capable of making the load setting of a spring finer and not causing a deviation after the setting.

A further object of the present invention is to provide a pressure regulating valve which can reliably maintain the set state after setting the spring load.

[0009]

In order to achieve the above first object, the present invention provides a valve body having an input port, an output port and a drain port, and slidably disposed in the valve body. A valve body for controlling mutual communication of the respective ports,
An electromagnetic solenoid for applying a load to the valve body and a spring are provided, and the valve body is slid to a balance position according to a load according to an input signal to the electromagnetic solenoid, a load by the spring and a feedback pressure, and input. A pressure regulating valve for regulating a supply pressure to a port to an output pressure and outputting the pressure from an output port, wherein the spring has a load setting means of the spring, the load setting means is screwed into the valve main body and the spring is set. And a holding member that is fixed to the valve body to prevent the receiving plug from rotating, and the receiving plug has an outer end portion in the rotational direction that engages with the holding member. An indexing portion is provided, and the holding member and the indexing portion of the receiving plug have a concave portion formed in one of them, and a convex portion that engages with the concave portion is formed in the other. When That.

In order to achieve the second object,
The holding member is configured to have a pair of leaf spring portions that sandwich the indexing portion of the receiving plug.

[0011]

In the structure according to claim 1 of the present invention, one of the holding member and the index portion formed in the receiving plug is provided with the concave portion and the other is provided with the convex portion. Since the engagement of these concave and convex portions achieves the rotation prevention function regardless of the size of the engaging surface, even if the indexing surface is subdivided to more accurately adjust the hydraulic pressure level, It is possible to reliably maintain the adjusted position of the receiving plug without causing the adjusted spring load to change due to the rotation of the receiving plug due to external force such as vibration.

Further, according to the second aspect of the present invention, the receiving plug is elastically held by the pair of leaf spring portions of the holding member in a well-balanced manner. The position of the received plug can be maintained.

[0013]

Embodiments of the present invention will be described below with reference to the drawings. First, FIG. 2 shows a cross section of a first embodiment of a pressure regulating valve to which the present invention is applied. In this example, the pressure adjusting valve is in the form of a linear solenoid valve (hereinafter referred to as a valve) for a hydraulic control device of an automatic transmission. Such a valve has a structure in which the electromagnetic portion S is fixed to one end of the pressure adjusting portion V, and is fitted into a valve hole penetrating the valve body of the automatic transmission in the thickness direction so that the electromagnetic portion S and the pressure adjusting portion V are connected. It is used in a position where the tip of the is exposed outside the valve body.

In this embodiment, the valve body of the pressure adjusting portion V is a sleeve 10, and a spool 20 as a valve body is slidably arranged in a spool sliding hole 11 that extends in the axial direction inside the sleeve. . The sleeve 10 includes a spool sliding hole 11 and five ports P1 formed at intervals in the axial direction.
.About.P5 and peripheral grooves 12 to 16 that communicate these ports with the spool sliding hole 11, the side on which the electromagnetic section S is attached has an enlarged diameter, and the opposite side has a reduced diameter.
The spool 20 has two large-diameter lands 21 and 22 and one small-diameter land 23 for communicating and blocking the adjacent circumferential grooves 12 to 16 via the spool sliding hole 11, and the surface of the electromagnetic section S is The side to be formed is a contact portion with a shaft described later. A spring 30 is disposed on the anti-electromagnetic portion S side in the spool sliding hole 11 of the sleeve 10, one end of which is in contact with a large-diameter land 22 of the spool 20 and the other end of which is a screw as a plug. It is brought into contact with the plug 40 and is supported in a compressed state. The screw plug 40 is screwed into a screw hole portion formed in an extension portion of the spool sliding hole 11, and at a position where a predetermined load is applied to the spool 20,
It is positioned and fixed by the load setting means according to the present invention.

The electromagnetic portion S has an enlarged diameter portion abutted against an enlarged diameter portion at one axial end of the sleeve 10, and a core 51 fixed to the sleeve 10 by caulking an inner end portion of the solenoid case 50.
A coil 52 that is attached to the case 50 so that it can be fitted around the outer periphery of the core 51, a plunger 53 that is arranged at the outer end of the core 51 so as to face the core 51, and a shaft that is fixed by caulking to the plunger 53. It is composed of an electromagnetic solenoid having 54. A linear ball bearing 55 that slidably supports the shaft 54 on the core 51 is disposed in the hollow portion of the core 51. In the figure, reference numeral 56 is a filter that also serves as a cushioning material for preventing the coil from floating, 57 is a spacer made of a non-magnetic material such as brass that maintains the minimum gap between the core 51 and the plunger 53, and 58 is an opening of the case 50. A cover plate 59 is a connector plug socket for connecting the coil 52 to an electronic control unit (not shown).

As shown in detail in an exploded perspective view in FIG. 1, the spring load setting means is fixed to the sleeve 10 and a screw plug 40 screwed into the sleeve 10 to support the spring 30 (see FIG. 2) in a compressed state. The retainer 60 serves as a holding member that prevents the screw plug 40 from rotating. The screw plug 40 has a dodecagonal indexing head 41 in the present embodiment, which constitutes an indexing portion for the retainer 60, on the outer end thereof. Further, the indexing head 41 of the retainer 60 and the screw plug 40 has a recess D formed in one of them (the indexing head 41 in the present embodiment) and the recess D in the other (the retainer 60 in the present embodiment). Convex part P to be engaged
Is formed.

As shown in the enlarged view of FIG. 3, the recess D formed in the indexing head 41 of the screw plug 40 is formed by recessing the indexing surface into a concave cylindrical surface in this embodiment. Particularly, in this embodiment, such a structure is adopted because such a surface structure is adopted in the screw plug 4
This is due to the manufacturing advantage that the die can be easily formed at the time of cold forging.

On the other hand, the retainer 60 is made of a spring material, and has a pair of fitting portions 61 in which a part of the snap ring-shaped base portion which constitutes the fixing portion to the sleeve 10 is reduced in diameter.
A pair of leaf springs 62 constituting the holding portion are connected to each other by a connecting portion 63 in the axial direction, and the connecting portion 63 is fitted to the chamfered portion 17 formed on the sleeve 10 to fit the snap ring-shaped base portion. 61 is fitted into a pair of circumferential openings 18 formed in the sleeve 10 to prevent rotation and axial removal. The convex portion P of the retainer 60 is a convex spherical projection that can be easily formed by press extrusion.

In the valve spring load setting means of the first embodiment having such a configuration, a hexagon wrench or the like is inserted into the fitting hole 43 formed in the center of the indexing head 41, and the screw plug 40 is appropriately inserted. Stroke in the axial direction by screwing in or unscrewing to change the compression amount of the spring 30 and set the load on the spool 20. At that time, the holding portion of the retainer 60 is elastically deformed and pushed away whenever the ridge angle of the indexing head 41 of the screw plug 40 exceeds the convex portion P, and allows the screw plug 40 to rotate with an appropriate torque load. Thus, the screw plug 40 can be re-set and operated while the valve is still installed in the valve body of the automatic transmission. After the setting, since the convex portion P presses the concave portion D by the spring elasticity, the receiving plug is not loosened by the vibration.

The operation of the valve of the first embodiment having such a configuration will be described with reference to FIG. 2 again for reference. In the state of no solenoid current load, the spool 20 and the spring 30
In the uppermost position shown in the figure under the load of, the output port P2 communicates with the input port P1 and the drain port P3 is cut off, and the supply pressure supplied from the input port P1 remains unchanged at the output port. While being output from P2, it is supplied to the circumferential groove 15 via the oil passage 24 in the spool, and is fed back as a secondary pressure to the diameter difference surface constituted by the land diameter difference between the large diameter land 21 and the small diameter land 23. It is balanced by a feedback pressure load that opposes the spring load.

When a signal current having a duty cycle corresponding to the control state is input to the coil 52 from an electronic control unit (not shown) for the valve in such a state, the plunger 53 is applied to the end portion of the core 51 by the electromagnetic attraction force. It is attracted toward the spool 20, and the accompanying load is transmitted to the spool 20 via the shaft 54.

Then, the spool 20 is displaced downward from the illustrated position, and the supply pressure supplied from the input port P1 is throttled by the land 21 to a predetermined pressure and output to the output port P2. The output pressure at this time is fed back as a secondary pressure to the radial difference surface between the land 21 and the land 23 via the oil passage 24 in the spool, and the output pressure is adjusted to a predetermined pressure by the balance of the solenoid load load, the spring load load, and the feedback pressure. keep. By the way, in this valve, the output pressure is reduced by increasing the duty cycle of the signal current.

In short, according to the valve of this embodiment, by forming the indexing surface into a concave cylindrical surface, the dodecagonal ridge angle can be made substantially equal to the conventional hexagonal ridge angle. The rotational torque required to exceed the ridge angle can be substantially the same as in the case of the conventional hexagonal ridge angle, and there is an advantage that the setting can be performed by the same method. Is secured in the same manner, and a moderate sense of moderation is obtained.

Next, FIG. 4 shows a modified example of the retainer 60 as a holding member of the spring load setting means of the above embodiment. In this example, the retainer 60 has a single leaf spring portion 6
2 is provided only on one side of the connecting portion 63. The rest of the configuration is the same as that of the holding member of the first embodiment, and therefore, corresponding members will be denoted by the same reference numerals and will not be described. When adopting such a configuration, by taking measures such as increasing the plate thickness of the retainer 60 as compared with the case of the above-described embodiment,
Substantially similar functions can be achieved.

Next, FIG. 5 shows a second embodiment. In this form, contrary to the form described above, the recess D is formed on the retainer 60 side, and the projection P is formed on the indexing head 41 side of the screw plug 40. In the case of this reverse arrangement, at least the recess D on the retainer 60 side must be a groove-shaped recess along the axis in order to allow the axial stroke of the screw plug 40. On the other hand, the convex portion P on the side of the screw plug 40 may be a dot-shaped projection or a cylindrical convex strip.

As described in detail above, in any of the above embodiments, the retainer 60 and the screw plug 40 are used.
The concave portion D in either one of the index portion formed in
However, since the convex portion P is provided on the other side, the engagement of the concave portion D and the convex portion P achieves the rotation preventing function regardless of the size of the engaging surface, so that the hydraulic pressure level is adjusted. Can be performed more accurately, and the adjusted spring load will not be displaced due to the screw plug 40 rotating due to external force such as vibration, and the adjusted position of the screw plug 40 can be reliably maintained. . When the screw plug 40 is sandwiched by the pair of leaf spring portions 62 of the retainer 60, the screw plug 4
No rattling of 0 is prevented, and the position of the screw plug 40 adjusted more reliably can be maintained.

Although the present invention has been described based on the two embodiments, the present invention is not limited to these embodiments, and various details can be obtained within the scope of the matters described in the claims. It does not prevent changing and implementing the concrete constitution of.

[Brief description of drawings]

FIG. 1 is an exploded perspective view showing a spring load setting means of a first embodiment of a pressure regulating valve to which the present invention is applied.

FIG. 2 is a sectional view of the pressure regulating valve.

FIG. 3 is an enlarged end view showing a spring load setting means of the pressure control valve.

FIG. 4 is a perspective view showing a modified example in which the holding member shape of the spring load setting means of the pressure regulating valve is changed.

FIG. 5 is an enlarged end view showing a spring load setting means in a second embodiment of the pressure regulating valve to which the present invention is applied.

FIG. 6 is an explanatory diagram showing a relationship between a signal current of a conventional pressure regulating valve and a prescribed value of pressure characteristics.

[Explanation of symbols]

 P1 input port P2 output port P3 drain port S Electromagnetic part (electromagnetic solenoid) 10 Sleeve (valve body) 20 Spool (valve body) 30 Spring 40 Screw plug (plug) 41 Indexing head (indexing part) 60 Retainer (holding) Member) 62 leaf spring part D concave part P convex part

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Takeya Oka 10 Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin AW Co., Ltd.

Claims (2)

[Claims] 1. A valve body having an input port, an output port and a drain port, a valve body slidably disposed in the valve body and controlling mutual communication of the respective ports, and the valve body. An electromagnetic solenoid for applying a load and a spring are provided, and the valve body is slid to a balance position corresponding to the load according to the input signal to the electromagnetic solenoid and the load by the spring and the feedback pressure, and is supplied to the input port. A pressure regulating valve for regulating a pressure to an output pressure and outputting the pressure from an output port, wherein the spring has a load setting means for the spring, the load setting means is screwed into the valve body to compress the spring. It comprises a receiving plug that supports and a holding member that is fixed to the valve body and that prevents the receiving plug from rotating. The receiving plug has a rotation method that engages with the holding member at its outer end. The holding member and the receiving plug have a concave portion formed on one of them and a convex portion that engages with the concave portion formed on the other. Pressure control valve characterized by. 2. The pressure regulating valve according to claim 1, wherein the holding member has a pair of leaf spring portions that sandwich the indexing portion of the receiving plug.